Gimballing flexure with static compensation and load print intregal etched features

ABSTRACT

A gimbal and corresponding head suspension assembly including a planar flexure platform having integral static attitude compensation, nominal angle adjustment, and load point etched or etched-formed raised features. The head suspension assembly can also include a load point cover with etched or etched-formed load point features. The etched features are manufactured by masking a pivot point at about the intersection of the roll axis and the pitch axis, thus leaving a raised protuberance having either a pivot point or a load point feature. The process of manufacturing etched-formed features includes etching protuberances and slots. A punch press is then applied to the protuberances. The slots help control the formation of raised domes and provide additional static compensation and nominal angle adjustment pivoting clearance.

BACKGROUND OF THE INVENTION

Standard head suspension assemblies (HSAs) include, as componentelements, a base plate, a load beam, a gimbal flexure and a headassembly. The load beam is an elongated metal spring structure. The baseplate is attached to a proximal end of the load beam, and can beconfigured for mounting the load beam to an actuator arm of a diskdrive. The gimbal flexure is positioned on a distal end of the loadbeam. Mounted to the gimbal flexure is a head assembly, which is therebysupported in read/write orientation with respect to an associated disk.The head assembly comprises a read/write transducer attached to an airbearing structure called a slider.

HSAs suspend the "flying" head assembly nanometers away from the surfaceof a rotatable data storage device (a spinning disk). The gimbal flexureprovides gimballing support, that is, the gimbal flexure positions andmaintains the head assembly at a desired flying attitude, apredetermined angle and height in relationship to the disk surface. Thestatic attitude of the head assembly, the position of the head assemblyat rest, is calibrated so that when the disk drive is in operation, andthe slider is affected by the lifting force of the air stream caused bythe rotation of the disk, the head assembly reaches an optimal dynamicattitude (position of the head assembly during operation).

To counter the air lift pressure exerted on the slider during disk driveoperation, a predetermined load is applied through a load point featureon the suspension assembly to a precise point on the slider. The headflies above the disk at a height established by the equilibrium of thesuspension force on the load point and the lift force of the air stream.

A conventional gimbal flexure, sometimes referred to as a Watrousgimballing flexure design, is formed from a single sheet of material andincludes a pair of outer flexible arms about a central aperture and across piece extending across and connecting the arms at a distal end ofthe flexure. A flexure tongue is joined to the cross piece and extendsfrom the cross piece into the aperture. A free end of the tongue iscentrally located between the flexible arms. The head assembly ismounted to the free end of the flexure tongue.

For optimum operation of the disk drive as a whole, during attachment ofthe slider to the flexure tongue, the mounting surface datum (to whichthe load beam is mounted during HSA assembly) and the slider air bearingsurface datum must be at a predetermined orientation with respect toeach other (desired relationship). The mounting surface datum and theslider air bearing surface datum are level surfaces used as referencepoints or surfaces in establishing the desired relationship of theactuator mounting surface and the slider air bearing surface relative toeach other (nominal angle). The upper and lower surfaces of the sliderare manufactured according to specifications requiring them to beessentially or nominally parallel to each other.

During the process of manufacturing and assembling the HSA, anydeviations caused by lack of precision in forming or assembling theindividual elements contributes to a lack of planarity in the surfacesof the elements. A buildup of deviations from tolerance limits in theindividual elements causes deviation from the desired relationship. Theparameters of static roll and static pitch torque in the HSA result fromthese inherent manufacturing and assembly tolerance buildups. The loadpoint feature of common gimbals does not compensate or help correctthese tolerance deviations.

Static roll torque and static pitch torque have their rotational axesabout the center of the head slider in perpendicular planar directions,and are caused by unequal forces acting to maintain the desiredrelationship on the slider while the head assembly is flying over thedisk. That is, static torque is defined as a torque or a moment of forcetending to cause rotation to a desired static (i.e., reference) attitudeabout a specific axis.

As applied to a HSA, the longitudinal axis of the slider is coincidentwith the longitudinal axis of the load beam and of the HSA. The axis ofroll torque is coincident with the longitudinal axis of the HSA. Thevalue of static roll torque is measured on either surface of the staticroll torque axis when the flexure tongue is parallel with the baseplate. If the flexure has been twisted about the static roll torque axisduring manufacture (i.e., there is planar non-parallelism of the flexuretongue with respect to the disk along the roll torque axis), the valuesmeasured on either surface of the roll torque axis will not be the same.Thus, when the attached slider is in flying attitude to the associateddisk surface, force (referred to as an induced roll torque value) isneeded to twist the tongue back into desired relationship alignment tothe disk.

The axis of pitch torque is perpendicular to the longitudinal axis ofthe HSA. The value of static pitch torque is measured on either surfaceof the static pitch torque axis when the flexure tongue is parallel withthe base plate. If the flexure has been twisted about the static pitchtorque axis during manufacture (i.e., there is planar non-parallelism ofthe flexure tongue with respect to the disk along the pitch torqueaxis), the values measured on either surface of the pitch torque axiswill not be the same. Thus, when the attached slider is in flyingattitude to the associated disk surface, force (referred to as aninduced pitch torque value) is needed to twist the tongue back intoparallel alignment to the disk. It will of course be understood that inactual static and dynamic attitude conditions the flexure can be twistedwith respect to both axes, requiring alignment about both the pitch axisand the roll axis.

These torques can also be referred to in terms of static attitude at theflexure/slider interface and in terms of the pitch and roll stiffness ofthe flexure. The ideal or desired pitch and roll torques are bestdefined as those which would exist if the components were installed inan ideal desired relationship configuration in a disk drive. In anactual disk drive, pitch and roll static torques produce adverse forcesbetween the air bearing surface of the slider and the disk, affectingthe flying height of the slider above the disk, resulting in deviationsfrom optimum read/write transducer and head assembly/disk interfaceseparation.

In the static attitude of a conventional flexure design, the flexuretongue is offset from the flexure toward the slider to allow gimballingclearance between the upper surface of the slider and the lower surfaceof the flexure. The offset is formed where the flexure tongue and crosspiece join, in conjunction with the dimple that is formed on the flexuretongue. Prior art dimples do not allow pivoting pitch and rolladjustments and act solely as load point features. The standard flexuredesign evidences a low value of pitch stiffness and a moderate value ofroll stiffness. Pitch stiffness and roll stiffness are each measured in(force×distance)/degree.

Thus, in developing a new design for a flexure, it would be mostdesirable achieve a precise method of fabrication and accuratelycompensate and correct for manufacturing variations that currentlycontribute to static pitch and roll torque errors. The manufacturingprocess should be efficient to perform corrections for static rolltorque, as well as for static pitch torque, since the ability to correctfor both static torques is needed for proper flexure/slider alignment.Ideally, the manufacturing process should also result in accurate andsimple placement of the load point feature.

Formation of pressure-formed surface features, such as dimples ordepressions, present accuracy difficulties. To increase manufacturingefficiency and ease of assembly, the number of additional components ina the flexure, especially small, delicate components, is preferablyreduced. Additional elements add complexity to the manufacturing processand present placement accuracy concerns. Only precise location of a loadpoint feature allows precise location of the slider flying surface; asthe dimple load point shifts from nominal the slider has a tendency tonot fly in the proper orientation relative to the disk due to the torqueresulting from the off-center load force. Thus, the manufacturingprocess of the ideal gimbal flexure should use very accuratemanufacturing techniques and reduce the number of additionalmanufacturing steps and added elements.

SUMMARY

The present invention is an improved gimbal and corresponding headsuspension assembly (HSA) that use etched integral features to providenominal angle adjustment, static attitude compensation, and a preciseload point feature alignment. The present gimbal is efficient tomanufacture and minimizes the use of separate components. The use of avery precise etching or etching-shaping process results in extremelyaccurate positioning of critical gimbal points for static attitudecompensation pivotting and load point features.

The head suspension assembly (HSA) comprises a suspension assembly and ahead assembly. The suspension assembly is comprised of a gimbal assemblyand a longitudinal spring element that has at least a portion stiffenedinto a load beam.

The present gimbal design includes a gimbal flexure platform supportedby gimbal spring arms. The platform has a slider engaging first surfaceand a second surface. During manufacturing, the platform is chemicallyetched out of a plate of stainless steel. During etching, a first raisedprotuberance is left at full or slightly reduced thickness on the firstsurface facing the slider. The first protuberance offers a preciselylocated slider contact point.

The slider of the head assembly attaches to the first surface of theflexure platform against the first protuberance. The protuberanceprovides a pivot feature for compensating adverse pitch and roll torquesresulting from pitch and roll static errors during manufacture andassembly and for providing nominal angle adjustment (adjusting the headassembly at a desired orientation).

In another embodiment of the invention the gimbal assembly also includesa bearing cover extending past the load beam and over the second surfaceof the flexure platform. The cover can be an extension of the load beamor a separate piece. The cover extends over the flexure platform andpresses against the platform at a bearing point that defines the pivotpoint of gimbal pitch and roll axes. The cover has an etchedprotuberance that acts as a load point feature to exert pressure on theslider. Different embodiments include round pressed dimples and raisedprotuberances combinations on the flexure platform and on the cover.

In still another embodiment, the flexure platform includes a first and asecond integral aligned protuberances rising from the first surface andthe second surface respectively. While the first protuberance acts as astatic attitude compensation and nominal angle adjustment feature, thesecond protuberance acts as a load point feature.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of a first surface of a head suspensionassembly in accordance with the present invention.

FIG. 2 is a detail perspective cut-away view of the gimbal of the headsuspension assembly of FIG. 1.

FIG. 3A is a plan view of the gimbal flexure platform of the gimbal ofFIG. 2 including a raised etched tower.

FIG. 3B is a view of a cross-sectional cut along lines B--B of FIG. 3A.

FIG. 4 is a perspective view of a second surface of the head suspensionassembly of FIG. 1.

FIG. 5 is a view of a cross-sectional cut of the gimbal of the headsuspension assembly of FIG. 1 along lines 5--5.

FIG. 6 is a view of a cross-sectional cut of the gimbal of the headsuspension assembly of FIG. 1 along lines 6--6.

FIG. 7 is a surface view of the load beam positioned along surface datumplane -A- and of the slider positioned along surface datum plane -B-.

FIG. 8 is a view of a cross-sectional cut along line 5--5 in FIG. 1,wherein the etched tower feature serves as a pivot to compensate fordesired relationship deviations.

FIGS. 9A-D show views of a cross-sectional cut of a flexure platformduring different steps in the manufacture of an embodiment of thepresent invention. FIGS. 9E-F show the same flexure platform includingconcentric radial slots.

FIGS. 10A-D show views of a cross-sectional cut of a flexure platformduring different steps in the manufacture of an embodiment of thepresent invention.

FIG. 11A shows a plan view of an etched tower and radial slots inaccordance with the present invention.

FIGS. 11B-C show different steps during the manufacturing process of theetched tower of FIG. 11A.

FIG. 12 is a perspective view of a head suspension assembly inaccordance with the present invention.

FIG. 13 is a view of a cross-sectional cut along line A--A in FIG. 12.

FIG. 14 is a view of a cross-sectional cut along line A--A of anembodiment of a head suspension assembly similar to the embodiment ofFIG. 12.

FIG. 15 is a perspective view of an embodiment of a head suspensionassembly in accordance with the present invention.

FIG. 16 is a view of a cross-sectional cut along line B--B in FIG. 15.

FIG. 17 is a view of a cross-sectional cut along line A--A of anembodiment of a head suspension assembly similar to the embodiment ofFIG. 12.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 shows the disk-facing surface of an assembled head suspensionassembly (HSA) 10. FIG. 4 shows the other surface of the same HSA 10.The HSA 10 comprises a suspension assembly 20 and a head assembly 30.The length of the HSA 10 defines a longitudinal axis 12 that bisects theHSA 10 down the middle. The suspension assembly 20 usually includes aload beam 22 and a gimbal assembly 50. The proximal end of thesuspension assembly 20 is reinforced by a base plate 24 that isconfigured for mounting to an actuator arm (not shown) used in some diskdrives.

FIG. 2 shows a detail cut-away view of the head assembly 30 attaching togimbal 50. Gimbal 50 can be integrally connected to the load beam 22 orcan be built as an independent element to be attached during HSAmanufacture. The gimbal 50 is manufactured by etching a planar plate ofa spring material, for example, stainless steel. Spring materials arethose that do not plastically deform (yield) under the most extremeloads applied during HSA use.

The head assembly 30 includes a transducer 32, mounted to a slider 34that has a disk facing air-bearing first major surface 36. The slider 34has an opposite second surface 38 that attaches to a gimbal flexureplatform 60.

Gimbal 50 is located at the distal end of the load beam 22. Gimbal 50includes spring arms 52 supporting the flexure platform 60 over acentral aperture. The flexure platform 60 is shaped and arranged tosupport the head assembly 30 and provide gimballing support.

Flexure platform 60 is a flat planar element and includes a firstsurface 62 and an opposite second surface 64, shown in FIG. 4. The firstsurface includes an etched protuberance 66 rising in the middle of theplatform 60. Protuberance 66 is ovoid shaped. Unlike pressure-formeddomes or dimples, protuberance 66 does not have an interior concavecavity, but is solid throughout. The flexure platform 60 is thicker atthe apex of protuberance 66 than anywhere else. In other embodiments,protuberance 66 can be shaped as a raised rectangular tower or asemisphere.

FIG. 3A shows a plan view of the gimbal of FIG. 2. Protuberance 66defines the pivot point of the pitch and roll axis of HSA 10. The pivotpoint is the actual point about which pitch and roll adjustments aremade, the actual intersection of pitch and roll axis of movement. Thepivot point is usually coincident with the geometrical intersection ofthe pitch axis and the roll axis of the slider 34. However, in someembodiments, the pivot point will be offset a few micrometers away fromthe geometrical intersection to compensate for different air streamspeeds along the inner part and the outer part of the air bearingsurface 36 of the slider 34.

A surface cut along line B--B is illustrated in FIG. 3B. The process ofmanufacturing gimbal 50 includes a first step of chemically etching aplate of stainless steel. While apertures and outer outlines are etchedthrough, features such as the spring arms 52 and flexure platforms 60are partially etched to a more flexible reduced thickness. Protuberance66 is shaped by masking a small point on flexure platform 60 whileetching the gimbal 50 and leaving the raised protuberance 66 at fullthickness or at only partially reduced thickness with respect to therest of the platform 50. A ring 65 with the same depth as the springarms 52 is etched around the protuberance 66. The ring 65 is shaped as amoat surrounding the protuberance 66 with reduced thickness. Etching ofthe ring 65 results in ease of processing when exposing and developingthe photoresist and the subsequent etching process. The ring 65 alsogives less variability to the placement of the protuberance 66.

FIG. 4 shows the second surface of gimbal 50 and of HSA 10. In thepresent embodiment, the whole suspension assembly is first etched outthe same sheet of stainless steel. Specific features such as rails 26 orwire guides 28 are shaped by bending and/or pressing specific etchedtabs.

As seen in FIGS. 5 and 6, when coupling the slider 34 to the flexureplatform 60, the protuberance 66 which protrudes ≈25 um from the firstsurface 62 provides a raised pivot interface to the second surface 38 ofthe slider 34 for eliminating adverse pitch and roll torques whichnormally result from pitch and roll static attitude errors. The secondsurface 38 of the slider 34 attaches to the platform 60 at the desiredangle. Once the desired angle is achieved, adhesive 68 fills the spacebetween the second surface 38 of the slider 34 and the flexure platform60.

During assembly of the HSA 10, the Reference Datum Planes -A- and -B-,shown in FIG. 7, are spaced a height Z and are positioned to achieve thedesired relationship. The suspension assembly 20 is aligned on datumplane -A- and the air bearing first surface 36 of slider 34 rests ondatum plane -B-. As shown in FIG. 8, the raised protuberance 66 servesas a pivot surface to allow for compensation along the pitch and rollaxis necessary to achieve the desired relationship. Using theprotuberance 66 as a swivel contact point, the nominal angle of theslider 34 can also be adjusted about either or both the pitch and rollaxis.

In order to illustrate how the raised protuberance corrects forsuspension static error, FIG. 8 shows adjustments to compensate for amisaligned or twisted flexure platform 60 along the roll axis. The planeof the flexure platform 60 is shown tilted an angle theta relative tothe air bearing first surface 36 of the slider 34. The etchedprotuberance 66 and adhesive 68 fill the space between the slider 34 andthe platform 60 to allow bonding at the twisted angle and prevent rolltorque. The gimbal interface allows for similar positioning tocompensate for both roll and pitch errors or to place the air-bearingsurface 36 of the slider 34 at a desired nominal angle with respect tothe surface of the disk. The resulting non-uniform bond line compensatesfor the non-planarity of the components and corrects static pitch androll torque errors. The etched protuberance 66 provides a means ofslider bonding which greatly reduces or entirely eliminates static pitchand roll torques due to static pitch and roll attitude errors andtolerances.

FIGS. 9-11 illustrate different steps in the manufacturing of differentembodiments of the present invention. FIG. 9 illustrates the manufactureof an embodiment, HSA 510, including a flexure platform 560 having afirst surface 562 and a second surface 564. The first step in themanufacturing process of the present embodiment comprises etching thegimbal platform including the raised protuberance 566. Etching providesmore accurate positioning of protuberance 566 than forming processes. Across-sectional cut of the flexure platform 560 after the etching stepis shown in FIG. 9A. A round punch-press 70, shown in FIG. 9B, is thenaligned with the vertical axis and applied against the second surface564 to shape a dome or dimple 542. The raised ovoid protuberance 566rises as a cupola from the apex of a dimple dome 542. FIG. 9D shows aslider 534 being attached at the correct angle to the flexure platform560 by an adhesive fill 568.

Radial concentric slots 554, shown in FIG. 9E can be etched partially ortotally around the protuberance 566 prior to applying the punch press.The width and depth of the slots 554 will vary according to the desiredsize and shape of the dome 542. FIG. 9F shows the dome 554 afterapplication of the punch press 70. The slots 554 help define and controlthe formed shape and size of the dome 542. The use of slots 554 resultsin better centering and less x-y variance in the positioning of the dome542, its apex, and protuberance 566, with respect to traditional formingonly techniques.

FIG. 10 illustrates manufacturing steps for another embodiment of thepresent invention. Gimbal flexure platform 660 is first chemicallyetched out of a plate of stainless steel. A raised control protuberance467 on a second surface 664 of the platform 660 is etched by masking thespot during etching. FIG. 10A shows the control protuberance 667 afterthe etching process. A flat punch press 72, shown in FIG. 10B, is thenapplied to the control protuberance 667 with enough force to create araised dome 666 on the first surface 662. The control protuberance 667acts as a forming control feature that helps define the formation of thedome 666. FIG. 10C shows the resulting domed flexure platform 660. Thecontrol protuberance 667 allows the use of the flat press 72. Use of theflat press 72, rather than a curve press such as in FIG. 9, makes exactalignment of the apex of the press with the vertical axis less crucial.Finally, a slider 634 is attached at the correct angle by adhesive fill668.

FIG. 11 illustrates manufacturing steps of another embodiment similar tothe embodiment of FIG. 10. In FIG. 11A, the second surface 764 of theflexure pad 760 is shown in plan view. Flexure platform 760 includesradial slots 754 concentric with the vertical axis etched around araised control protuberance 767. The slots 754 can be etched through orhave reduced thickness with respect to the surface of the flexureplatform 760. FIG. 11B shows a flat punch press 72 applied against theraised control protuberance 767. The punch press 72 creates anotherraised dome 766 on the first surface 762 of the flexure platform 760.Control protuberance 767 allows the use of the flat press 72 and helpsdefine the shape of the dome 766. The slots 754 control the deformationof the dome 766 during the punching process and help define the shapeand size of the dome 766.

FIG. 12 shows a second embodiment of an HSA 210 in accordance with thepresent invention. The embodiment includes a gimbal plate 250 attachedto and extending past the distal end of load beam 222. The gimbal plate250 includes a rectangular flexure platform or tongue 260 suspended atits distal end by two spring arms 252. As better seen on FIG. 13, across-sectional cut along line A--A, platform 260 has a disk-facingfirst surface 262 and a second surface 264. A load beam cover 240extends from the distal end of the load beam 222, opposite the secondsurface 264 of platform 260. The cover 240 can be an integral projectionof the load beam 222, such as the rectangular "T" projection of thepresent embodiment, or can be a separate element attached (by adhesive,welds, or other methods known in the art) to the load beam 222. Thegimbal plate 250 also can be an integral projection of the load beam 222or can be a separate element attached (by adhesive, welds, or othermethods known in the art) to the load beam 222. The cover 240 extendsover a portion of the flexure platform 260 and over the etchedprotuberance 266.

As seen in FIG. 13, the cover 240 includes a punch-pressed dimple 242 (aload point feature) that contacts the second surface 264 of the flexureplatform 260 and presses against it, thus defining the load point. Thepunch-pressed dimple 242 is aligned along the same vertical axis as theprotuberance 266.

In the embodiment shown in FIG. 14, the cover 340 includes an etchedprotuberance 366, while the flexure platform includes a punched dimple342. The corresponding concave surface of the dimple 342 accommodatesthe protuberance 366 and allows for the proper static attitudecompensation. In still other embodiments, such as that of FIG. 9, thedome 542 is capped by another protuberance to allow for greater attitudecompensation clearance.

The HSA 410 of FIG. 15 is similar to the HSA 310 of FIG. 12. FIG. 16, across-sectional cut along line B--B, shows cover 440 pressing against aflexure platform 460. Flexure platform 460 includes two oppositelyaligned raised etched protuberances 466 and 467. Both protuberances arealigned along the same vertical axis that is orthogonal to the pitchaxis and the roll axis. First protuberance 466 rises from a firstsurface 462 of the flexure platform 460, while second protuberance 467rises from the second surface 464 of flexure platform 460. In thepresent embodiment, the first protuberance 466 acts as a static attitudecompensation and adjustment feature, while the second protuberance 467acts as a load beam interface load point feature. Use of the secondprotuberance 467 as a load point feature eliminates accuracy andmanufacturing concerns of exactly aligning a separate load point featureon the load beam cover 440 with the vertical axis and the firstprotuberance 466.

The etching and the etching-forming procedures provide exceptionalpositioning accuracy and centering for the static attitude compensationand load point features. The described manufacturing processes can beapplied to the manufacture of very accurate load point features as wellas attitude compensation features.

FIG. 17 shows a cross-sectional cut along line A--A of an embodiment ofa head suspension assembly similar to the embodiment of FIG. 12. Cover840 includes a formed raised dome 842 capped at its apex by an etchedprotuberance 866. The cover 840 is manufactured by the processesillustrated in FIGS. 9A-F. The x-y positioning variance of protuberance866 is minimal, and the raised dome 842 gives the load point featureadded offset clearance for static attitude compensation and nominalangle adjustment.

Another embodiment (not shown) includes a load beam cover with across-section similar to that of the flexure platform 660 shown in FIG.10C. The cover includes a first surface facing a flexure platform, thesurface having a raised dome. The second surface of the cover includesan inside concave surface with a protuberance. Following the samegeneral etching-shaping process applied to the embodiment of FIG. 10,the cover is first etched, leaving the raised central protuberancealigned along the vertical axis on the second surface. Concentric slotscan be etched around the protuberance. A flat punch press is applied tothe protuberance, thus creating the raised dome. The dome then acts as aload point feature.

The invention is not to be taken as limited to all of the detailsthereof as modifications and variations thereof may be made withoutdeparting from the spirit or scope of the invention.

What is claimed is:
 1. A head suspension assembly for supporting a headassembly at a predetermined flying attitude with respect to the surfaceof a rotatable data storage device, the head suspension assemblycomprising:a load beam comprising an elongated spring structure; a headassembly including a transducer and a slider; a gimbal located at thedistal end of the load beam, the gimbal including a resilient and planarload bearing flexure platform which is able to flex to permit the sliderto move in pitch and roll directions during operation over a disksurface, said flexure platform having a slider-engaging first surfaceand a second opposite surface, and wherein the platform is etched toleave an integral solid static attitude compensation protuberanceextending from the first surface with a corresponding flat portion ofsaid second opposite surface; and a layer of adhesive for bonding theslider to the first surface of the flexure platform, wherein the staticattitude compensation protuberance contacts the slider, and the adhesivefills interstitial spaces between the slider and the platform which havebeen formed by the contact between the static attitude compensationprotuberance and the slider to prevent pitch and roll movements aboutthe static attitude protuberance during operation over a disk surfaceand rigidly hold the slider at a desired static attitude with respect tothe first surface of the flexure platform.
 2. The head suspensionassembly of claim 1, the flexure platform of the gimbal furtherincluding an etched integral solid load point protuberance on the secondsurface, the load point protuberance extending from the second surface.3. The head suspension assembly of claim 4 wherein the flexure platformfurther includes a dome surrounded by the ring and having a convexsurface extending from the first surface of the flexure platform, andwherein the static attitude compensation protuberance rises from theconvex surface of the dome.
 4. The head suspension assembly of claim 1,the flexure platform of the gimbal further including a ring etchedaround the static attitude compensation protuberance.
 5. The headsuspension assembly of claim 1, further comprising a load point cover,the load point cover located on the distal end of the load beam andengaged with at least a portion of the second surface of the flexureplatform.
 6. The head suspension assembly of claim 5, wherein the loadpoint cover includes a convex dome engaged with the second surface ofthe flexure platform.
 7. The head suspension assembly of claim 1 whereinthe flexure platform further includes a dome having a convex surfaceextending from the first surface of the flexure platform, and whereinthe static attitude compensation protuberance rises from the convexsurface of the dome.